WO2010052044A1 - Soufflante à canal latéral, en particulier turbine secondaire pour un moteur à combustion interne - Google Patents

Soufflante à canal latéral, en particulier turbine secondaire pour un moteur à combustion interne Download PDF

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Publication number
WO2010052044A1
WO2010052044A1 PCT/EP2009/061514 EP2009061514W WO2010052044A1 WO 2010052044 A1 WO2010052044 A1 WO 2010052044A1 EP 2009061514 W EP2009061514 W EP 2009061514W WO 2010052044 A1 WO2010052044 A1 WO 2010052044A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
blower
inlet
channel
region
Prior art date
Application number
PCT/EP2009/061514
Other languages
German (de)
English (en)
Inventor
Berthold Herrmann
Andreas Bumbel
Jakob Gehlen
Mario Kilzer
Martin Miokowski
Rainer Peters
Thomas Rösgen
Original Assignee
Pierburg Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Pierburg Gmbh filed Critical Pierburg Gmbh
Priority to EP09782660.6A priority Critical patent/EP2342465B1/fr
Publication of WO2010052044A1 publication Critical patent/WO2010052044A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/008—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/007—Details of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/50—Inlet or outlet
    • F05B2250/503—Inlet or outlet of regenerative pumps

Definitions

  • the invention relates to a side channel blower, in particular secondary air blower for an internal combustion engine with a housing in which an outlet is formed, a first housing part, in which an axial inlet is formed, which opens via an inlet region in a first, substantially annularly extending conveying channel, an impeller which is drivable via a drive unit, is rotatably mounted in the housing and has conveying blades, which cooperate with the opposite conveyor channel, an interruption area between the inlet and the outlet, in which the conveyor channel is interrupted in the circumferential direction, and a recess which in Direction of rotation of the impeller is formed in front of the inlet region at the interruption region and is fluidly connected to the inlet region.
  • Running direction of the impeller are as far apart as possible, with a
  • Interruption area is to be prevented.
  • the high noise has been found, which arises in particular by pulsations caused by sudden
  • Inlet area can suddenly relax towards the inlet in the inlet area. This leads both to a poorer efficiency of the pump and to significantly increased noise emissions.
  • DE 10 2004 019 868 A1 proposes a fan in which the interruption area is designed in such a way that the pockets sweeping over the interruption area are not opened at the same time over their entire cross-section, but first only in their radial outer area and only then as the movement progresses, a further opening of the pockets also follows in the radially inner region.
  • the inlet itself is arranged in the radially inner region, so that the expansion of the delivered fluid does not take place directly above the inlet.
  • the inlet is partially covered by the interruption area.
  • noise even though reduced, is created by pressure pulsations because sudden cross-sectional changes occur downstream of the break region for partial volumes of the volume delivered in the pockets upon reaching the inlet region.
  • These pressure pulsations continue from radially outward to radially inward as they reach the inlet region through the respective part of the pocket.
  • This object is achieved in that the depth of the recess from the impeller facing the upper edge of the interruption area grows toward the inlet area. As a result, a sudden relaxation of a partial volume of the conveyed between the blades and air thus resulting pressure pulsations is reliably avoided.
  • the air conveyed over the interruption area can relax steadily with rotation of the impeller. A restriction of the inlet cross-section of the inlet is no longer required, so that larger amounts of air can be sucked.
  • the recess is in the form of a chamfer extending from the interruption region in the direction of the inlet. This form provides a steady extension of the cross-section for the air delivered over the break region for slow continuous relaxation.
  • the width of the recess is equal to the width of the conveyor channel. In this way, pressure pulsations can be further reduced, since the volume is continuously increased over the entire relevant flow cross-section of the conveyor blade interspace lying opposite the recess. It when the length of the recess in the circumferential direction is greater than the distance between two successive blades of the impeller is particularly advantageous. In such an embodiment, it is ensured that first of all a relaxation of the entire volume conveyed over the interruption region takes place before the entire cross section of the inlet region is made available to a partial volume, which would again lead to a change in flow and thus to pressure pulsations.
  • the length of the recess in the circumferential direction corresponds to> 1 times the distance between two successive blades of the impeller.
  • the diameter of the inlet region is greater than the width of the conveying channel, wherein the shortest distance of an inner edge of the inlet region is equal to the distance of the inner edge of the conveying channel.
  • the housing consists of the first housing part, which serves as a cover part, and at least a second housing part in which a second substantially annular extending delivery channel is arranged, which opens into the outlet, which is arranged tangentially to the second housing part, wherein the conveying blades of the impeller facing the delivery channels to both axial sides of the impeller.
  • This version is a two-channel blower, which further improves efficiency compared to single-duct blowers. It is thus a side channel blower created in which compared to known side channel blowers the flow rate can be increased with the same size of the pump and at the same time outwardly urgent noise can be largely avoided by occurring pressure pulsations.
  • Figure 1 shows a side view of a side channel blower in a sectional view.
  • FIG. 2 shows a perspective view of the cover part of the side channel blower according to the invention from FIG. 1.
  • Figure 3 shows a plan view of the lid part according to the figure 2 from the direction of the impeller.
  • FIG. 4 shows a sectional illustration along the section line A-A of FIG. 3.
  • FIG. 5 shows a sectional illustration along the section line B-B of FIG. 3.
  • the side channel blower shown in Figure 1 consists of a two-part housing 2 and a rotatably mounted in the housing 2 and driven by a drive unit 3 impeller 4, for example for the promotion of air.
  • the air passes via an axial inlet 6 into an inlet region 8 of a first housing part 10, which serves in the present embodiment as a cover part of the side channel blower. From the inlet region 8, the air then flows into two substantially annularly extending conveying channels 12, 14, of which the first conveying channel 12 is formed in the cover part 10 and the second conveying channel 14 is formed in a second housing part 16, in which also a bearing 18 a drive shaft 19 of the drive unit 3 is arranged, on which the impeller 4 is fixed.
  • the exit of the air takes place via a tangential outlet 20, which is arranged on the second housing part 16.
  • the impeller 4 is disposed between the cover member 10 and the second housing member 16 and has at its periphery conveying blades 22 which are curved and extend radially, wherein the conveying blades 22 by a radially extending peripheral ring 24 in a first row axially opposite to the first Delivery channel 12 and a second row axially opposite to the second conveying channel 14 are divided, so that two swirl ducts are formed, which are each formed by one of the conveying channels 12, 14 with the facing part of the impeller 4.
  • the outer diameter of the conveying channels 12, 14 is slightly larger than the outer diameter of the impeller 4, so that a fluidic connection between the two conveying channels 12, 14 outside the outer periphery of the impeller 4 is made. Between the extending from the peripheral ring 24 conveyor blades 22 are thus formed radially outwardly open pockets 26, in which the air is promoted or accelerated.
  • Cover part 10 and arranged on the housing part 16, in which the delivery channels 12, 14 are interrupted, so that in the interruption region 28 axially opposite to the conveying blades 22 of the impeller 4 as small a gap as possible.
  • the delivery channel 12 arranged in the cover part 10 has a substantially constant width b and coincides with
  • interruption region 28 extends over the circumference of the lid part. In the view selected here, thus, the impeller 4 rotates in
  • the cover part 10 is fastened by means of screws to the second housing part 16, which are inserted through corresponding bores 30 which are formed on radially outwardly extending projections 32 on the cover part 10. At two of these projections 32 are additionally small, axially extending bolts 34, which serve for the prefixing of the cover part 10 on the second housing part 16.
  • a groove 38 is formed in the seal between the cover part 10 and the second housing part 16, a sealing ring 40 is inserted, which is held by lugs 42 in the groove 38.
  • an annular ridge 46 is formed, which engages after assembly of the fan in a corresponding groove 48 of the impeller 4, whereby a seal from the conveying channel 12 in the direction of the interior of the impeller 4 takes place.
  • the cover part 13 has a cylindrical recess 50 into which the drive shaft 19 of the drive unit 3 protrudes.
  • a recess 52 is formed in front of the inlet region 8, which extends from an upper edge 54 of the interruption region 28 in the direction of the inlet region 8.
  • the recess 52 is designed so that its cross-sectional area grows steadily in the direction of the inlet region 8, wherein in the present embodiment, the width b of the recess 52 over the entire length about the width b of the conveying channel 12 corresponds, so that the growing cross-section by a change the depth is realized, which grows to the inlet portion 8 to a depth corresponding to the depth of the conveying channel 12.
  • the recess 52 thus has a constant angle to the surface of the interruption region 28, so that it is formed substantially as a chamfer.
  • An end region 54 of the delivery channel 12 is formed substantially corresponding to the tangential outlet 20, so that the end wall 56 delimiting the channel 12 substantially forms an extension of the outlet 12.
  • the inlet 6 has to increase the delivery volume has a diameter d which is greater than the width b of the conveying channel 12, wherein an inner edge 58 of the inlet portion 8 is disposed at an equal radius as an inner edge 59 of the conveying channel 12, so that the cover part 10th in the inlet region 8 has a larger circumference than in the other areas.
  • This also has the consequence that the recess 52 does not extend over the entire diameter d of the inlet region 8, but the recess 52 is bounded by a radially delimiting outer wall 60, which extends substantially axially.
  • a front edge 62 which forms the line of intersection of the interruption region 28 with the recess 52, formed arcuate, so that the conveyor blades 22 of the impeller 4, the recess 52 first in the radially outer region and then in the radially inner region.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne des ventilateurs à canal latéral dotés de dispositifs permettant de réduire les émissions sonores, lesquelles sont souvent insuffisants et limitent le débit volumétrique souhaité. A cet effet, un ventilateur à canal latéral comportant une entaille est utilisé, et il est placé dans le sens de rotation du rotor de la soufflante (4) devant la partie d'admission (8) sur la partie de blocage (28) et il est en communication fluidique avec la partie d'admission (8). Selon l'invention, la profondeur de l'entaille (52) du bord supérieur (54) de la partie de blocage (28), tournée vers le rotor de la soufflante (4) s'accroît vers la partie d'admission (8). Ainsi, le bruit peut être réduit et le débit volumétrique souhaité augmenté.
PCT/EP2009/061514 2008-11-06 2009-09-07 Soufflante à canal latéral, en particulier turbine secondaire pour un moteur à combustion interne WO2010052044A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP09782660.6A EP2342465B1 (fr) 2008-11-06 2009-09-07 Soufflante à canal latéral, en particulier turbine secondaire pour un moteur à combustion interne

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008056105A DE102008056105B4 (de) 2008-11-06 2008-11-06 Seitenkanalgebläse, insbesondere Sekundärluftgebläse für eine Verbrennungskraftmaschine
DE102008056105.3 2008-11-06

Publications (1)

Publication Number Publication Date
WO2010052044A1 true WO2010052044A1 (fr) 2010-05-14

Family

ID=41571300

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/061514 WO2010052044A1 (fr) 2008-11-06 2009-09-07 Soufflante à canal latéral, en particulier turbine secondaire pour un moteur à combustion interne

Country Status (3)

Country Link
EP (1) EP2342465B1 (fr)
DE (1) DE102008056105B4 (fr)
WO (1) WO2010052044A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103154523A (zh) * 2010-09-29 2013-06-12 皮尔伯格有限责任公司 侧通道鼓风机，尤其是用于内燃机的次级空气鼓风机
CN105683580A (zh) * 2013-10-14 2016-06-15 大陆汽车有限责任公司 用于特别设计为侧通道鼓风机的侧通道流体机械的叶轮

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE902074C (de) * 1937-08-08 1954-01-18 Fritz Oesterlen Dr Ing Umlaufverdichter mit einem gleichachsig zum Laufrad gelegenen Seitenkanal
US3252421A (en) * 1962-10-16 1966-05-24 Siemen & Hinsch Gmbh Pumps
US3356033A (en) * 1965-10-22 1967-12-05 Ford Motor Co Centrifugal fluid pump
US3982848A (en) 1974-02-26 1976-09-28 Siemens Aktiengesellschaft Side channel ring compressor including a channel break decompression nozzle
DE2531740A1 (de) * 1975-07-16 1977-02-03 British Gas Corp Umfangsgeblaese
EP0332078A1 (fr) * 1988-03-06 1989-09-13 Webasto AG Fahrzeugtechnik Soufflante à canal latéral
EP0586934A1 (fr) * 1992-09-08 1994-03-16 Firma J. Eberspächer Soufflante à canal latéral avec génération de bruit reduit
DE4424629C1 (de) * 1994-07-13 1995-03-09 Becker Kg Gebr Seitenkanalverdichter
DE102004019868A1 (de) 2004-04-23 2005-11-24 J. Eberspächer GmbH & Co. KG Gebläse, insbesondere Verbrennungsluftgebläse für ein Heizgerät

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE902074C (de) * 1937-08-08 1954-01-18 Fritz Oesterlen Dr Ing Umlaufverdichter mit einem gleichachsig zum Laufrad gelegenen Seitenkanal
US3252421A (en) * 1962-10-16 1966-05-24 Siemen & Hinsch Gmbh Pumps
US3356033A (en) * 1965-10-22 1967-12-05 Ford Motor Co Centrifugal fluid pump
US3982848A (en) 1974-02-26 1976-09-28 Siemens Aktiengesellschaft Side channel ring compressor including a channel break decompression nozzle
DE2531740A1 (de) * 1975-07-16 1977-02-03 British Gas Corp Umfangsgeblaese
EP0332078A1 (fr) * 1988-03-06 1989-09-13 Webasto AG Fahrzeugtechnik Soufflante à canal latéral
EP0586934A1 (fr) * 1992-09-08 1994-03-16 Firma J. Eberspächer Soufflante à canal latéral avec génération de bruit reduit
DE4424629C1 (de) * 1994-07-13 1995-03-09 Becker Kg Gebr Seitenkanalverdichter
DE102004019868A1 (de) 2004-04-23 2005-11-24 J. Eberspächer GmbH & Co. KG Gebläse, insbesondere Verbrennungsluftgebläse für ein Heizgerät

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103154523A (zh) * 2010-09-29 2013-06-12 皮尔伯格有限责任公司 侧通道鼓风机，尤其是用于内燃机的次级空气鼓风机
CN103154523B (zh) * 2010-09-29 2015-10-14 皮尔伯格有限责任公司 侧通道鼓风机,尤其是用于内燃机的次级空气鼓风机
US9297276B2 (en) 2010-09-29 2016-03-29 Pierburg Gmbh Side channel blower, in particular a secondary air blower for an internal combustion machine
CN105683580A (zh) * 2013-10-14 2016-06-15 大陆汽车有限责任公司 用于特别设计为侧通道鼓风机的侧通道流体机械的叶轮
US10273960B2 (en) 2013-10-14 2019-04-30 Continental Automotive Gmbh Impeller for a side channel flow machine in particular designed as a side channel blower

Also Published As

Publication number Publication date
EP2342465B1 (fr) 2019-09-04
EP2342465A1 (fr) 2011-07-13
DE102008056105B4 (de) 2011-02-03
DE102008056105A1 (de) 2010-05-20

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